Rotary machine having vanes



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ROTARY MACHINE HAVING VANES Filed Oct. 1, l962 5 Sheets-Sheet 5 June 14, 1966 K. EICKMANN 3,255,705

ROTARY MACHINE HAVING VANES Filed Oct. 1, 1962 5 Sheets-Sheet 4.

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5-4 ad ./7 may United States Patent 3,255,705 RUTARY MACHINE HAVING VANES Karl Eickmann, 2420 lsshiki, Hayama-machi, Miuragun, Kanagawa-lren, Japan Filed 0st. 1, 1962, Ser. No. 229,259 28 Claims. (Cl. 103-138) The present invention relates to a rotary machine having vanes, and more particularly to a rotary machine operated by a fluid as a pump or motor, and having radially movable vanes forming contracting and expanding chambers for the fluid.

It is one object of the present invention to improve known. rotary machines of this type, and to. provide a rotary machine operating at low friction and with a high torque.

Another object of the present invention is to permit a stator part which is in sliding sealing contact with the rotor, to wobble with the rotor so that the seal between the rotor and the stator part is maintained even under high pressure.

Another object of the invention is to provide flexible inlet means and outlet means permitting a slight relative movement between the stator and the rotor of the machine, while maintaining the inlet and outlet passages tightly sealed.

Another object of the invention is to maintain an equilibrium between all inwardly directed pressure forces exerted by the pressure fluid on the rotor.

Another object of the invention is to provide a stator member formed with recesses through which the vanes pass during rotation of the rotor so that contracting and expanding chambers are formed between each vane means, the surfaces of the respective recess, and the outer surface of the rotor.

Another object of the invention is to guide the moving vanes in a simple but reliable manner in the rotor.

Another object of the invention is to move the vanes inwardly and outwardly by hydraulic control means so that the friction between the vanes and the innerstator surface engaged by the vanes is reduced or eliminated.

With these objects in view, one embodiment of the invention comprises rotor means including a plurality of radially movable vane means, and having an inner surface surrounding the rotor means and being formed with a plurality of recesses equally spaced in circumferential direction and successively passed by the vane means during rotation of therotor means. Consequently, each vane means forms in each recess an expanding chamber and a contracting chamber which are respectively equally spaced in circumferential direction from the other expanding and contracting chambers. In the preferred embodiment of the invention, each expanding chamber is located diametrically opposite another expanding chamber, and each contracting chamber is located diametrically opposite another contracting chamber. In this manner, all inwardly directed pressures exerted by the fluid in the chambers, are in equilibrium.

In the preferred embodiment of the invention, the rotor means includes a center portion, and a pair of end members, and the vane means are guided in the center portion and in the end members. The end members have confronting annular guide faces in sliding and sealing engagement with opposite annular guide faces on a stator member which surrounds the center portion of the rotor.

Preferably, the stator member is mounted in such a manner that it can perform a limited spherical or wobbling motion so that the annular guide faces of the rotor and stator remain in sealing contact when the rotor means wobbles.

Due to the fact that the stator member and the. rotor "ice means are mounted for relative movement, which is preferably accomplished by a loosely mounted floating ring, the inlet and outlet openings in the stator and in the rotor move relative to each other, and consequently flexible tubular inlet and outlet means are provided in accordance with the present invention to permit relative movement of the stator and casing, while providing for a fluid tight admission and discharge of fluid.

In a modified embodiment of the invention, cylinder and piston means are provided in the end members of the rotor, and connected to the vane means to move the same in inward and outward direction whereby the friction between the outer end of the vane means and the inner surface of the stator member is reduced.

The novel features which are considered as characteristic for the invention are set forth in particular in the appended claims. The invention itself, however, both as to its construction and its method of operation, together with additional objects and advantages thereof, will be best understood from the following description of specific embodiments when read in connection with the accompanying drawings, in which:

FIG. 1 is an axial sectional view of one embodiment of the invention;

FIG. 2 is a cross sectional view taken on line IIII in FIG. 1;

FIG. 3 is an axial sectional view of another embodiment of the invention; I

FIG. 4 is a cross sectional view taken on line IV in FIG. 3;

FIG. 5 is a fragmentary sectional view taken on line VV in FIG. 2; and

FIG. 6 is a fragmentary sectional view on an enlarged scale taken on line VIVI in FIG. 5.

Referring now to the drawings, and more particularly to FIGS. 1 and 2, a rotor 1 is located within an outer casing 46 and includes a shaft 51 which is supported in bearings 54 in casing 46. A split ring 57 secures the bearing 54, and an annular sealing means 56 is provided between the casing 46 and the end plate 59 of the rotor, while the other end plate 60 abuts the other bearing 54. A balancing chamber 55 is provided between members 56 and 59, and is filled with fluid to maintain the rotor in position. Inwardly of end plates 59 and 60, a pair of outer rotor members 102 and 103 are located, which are formed with radial slots 302 and 303 closed at the outer end thereof by annular members 79. Members 59, 103, and 79, constitute one end member, and members 60, 102 and 79 constitute the other end member of the rotor. The center portion of the rotor has radially extending outwardly open guide slots 3 which register with the closed guide slots 302 and 303 to form with the same guideways for vane means 4 having end portions 402 and 403 which are respectively guided in guide slots 302 and 303. Spring means 6 are mounted in corresponding recesses of members 102 and 103, and abut the end portions of the vane means so that the vane means are urged in outward direction until abutting the annular members 79. The end portions of the vane means 4 are recessed and narrow where the springs 6 abut, but since the end portions 402 and 403 are guided in slots 302 and 303, the center portions of the vane means which are subjected to fluid pressure can have the full radial width.

An annular stator member 2 surrounds the center portion of rotor 1, and has annular guide faces 201 and 202 located in planes transverse to the rotor axis, and in sliding engagement with confronting annular guide faces 179 of the annular members 79. Communication passages in the rotor means connect the innermost parts of the guide slots 302, 303 with at least one of the confronting guide faces 179.

As best seen in FIGS. 5 and 6, recesses 75 are provided on the annular guide faces 201 and 202, and are filled with fluid to reduce the friction between the rotor guide faces 179 and the stator guide faces 201, 202. The recesses 75 may also be provided in the surfaces 179 of the rotor. Each recess 75 has a pair of inclined bottom surfaces 76 extending at a very small angle, which is shown in an exaggerated manner in FIG. 6. Leakage fluid collects within recesses 75 during operation of the machine, and since the rotor guide faces 179 move relative to the stator guide faces 201 and 202, fluid particles of the fluid in the recesses 75 are pressed between the guide faces while the same move relative to each other in accordance with the physical law of shearing of fluid. In this manner, a high pressure acting normal to the contacting guide faces is produced adjacent the inclined surfaces 76 or 77. In the direction of rotation indicated by an arrow in FIG. 6, fluid will be pressed into the region between the guide faces adjacent the inclined face 76. Outlets ducts 78 are provided in the regions of the ends of the recesses and are arranged to communicate with spaces in the machine which are under low pressure, for example with the interior of the outer casing 46.

If the gap or clearance between adjacent rotor and stator guide faces becomes very small, no fluid can pass from recess 75 to the duct means 78. Consequently, the hydro-dynamic pressure forces appearing on the inclined surfaces 76 or 77 will tend to urge the two guide faces away from each other. The gap or clearance on the other side of the stator member 2 is correspondingly larger, and consequently fluid will flow through the larger clearance from the respective recess 75 to the respective duct 78. In this manner, the resultant of the forces produced by the fluid flowing through the larger clearance is reduced, and becomes smaller than the hydro-dynamic force acting in the smaller clearance on the other side of the stator member 2 until equal clearances are obtained on opposite sides of the stator member 2 whereby leakage between stator member 2, and rotor members 79 is reduced to a minimum, and the efliciency of the machine is correspondingly increased.

As best seen in FIG. 2, stator member 2 is provided with diametrically opposite recesses, each recess having a part-cylindrical surface 74, and two inclined surfaces 72 and 73. During rotation of the rotor, the vanes 4 pass in circumferential direction through the recesses in the stator, and form in the same chambers 41 and 42 located in opposite sides of the vanes, and expanding and contracting, respectively during rotation. If the rotor 1 rotates in clockwise direction as viewed in FIG. 2, as indicated by an arrow, spaces 42 and 40 will be reduced in volume and contract, while spaces 39 and 41 will increase in volume and expand.

If the machine is used as a motor, pressure fluid will be admitted to the expanding chambers 39 and 41, and the fluid will be discharged from the contracting chambers 42 and 40. If the machine is used as a pump, high pressure will prevail in the contracting chambers 40 and 42 and lower pressure will prevail in the expanding chambers 39 and 41.

The recesses have open ends which are closed by the end members of the rotor, and more particularly by members 59 and 60. Only two recesses and pairs of chambers are illustrated in the drawing, but it will be understood that a greater number of recesses can be provided equally spaced in circumferential direction from each other so that the inward pressures produced in the high pressure chambers, but also in the low pressure chambers are balanced and the forces acting on the rotor are in equilibrium.

Due to this balancing of the pressure forces in combination with other features of the invention, it is possible to produce far higher pressures in the machine of the present invention than in conventional machines. However, if the pressure and torque is increased, difliculties arise since the higher pressure tends to produce greater leakage. The annular gaps 58 between the stator guide faces 201, 202 and the rotor guide faces 179 must be extremely small to avoid high leakage losses.

If rotor 1 would rotate in a very precise motion about its axis, the gap 58 could be reduced to a minimum and the leakage correspondingly reduced. However, under practical conditions, the rotor performs a slight wobbling motion, and portions of the rotor guide faces 179 move alternately in opposite axial directions.

In order to maintain the annular guide faces 179 in sealing contact with the guide faces 201 and 202 of the stator member 2, in accordance with the present invention the stator member 2 is mounted in such a manner on the supporting casing 46 that the stator member 2 is capable of performing a slight and limited wobbling motion together with the rotor 1. Such Wobbling motion of stator member 2 is possible if stator member 2 is mounted on casing 46 for limited tilting movement about two perpendicular axes which are also perpendicular to the axis of the rotor, and also for limited axial movement. Such a mounting of stator member 2 will permit a movement of the inner surface 74 of stator member 2 along an imaginary spherical surface.

As best seen in FIG. 2, stator member 2 has a pair of diametrically arranged axially extending guideways 7 in which slide shoes 13 are mounted for axial sliding movement. A pin 12 is secured to each slide shoe 13, and projects into a corresponding radial bore 9 in a floating ring 8 which surrounds stator member 2, a small gap being provided between stator member 2 and floating ring 8 to permit relative movement in radial direction and in the direction of the common axis of pins 12 while the latter move in bores 9.

A pair of diametrically opposite pins 11 is secured to the casing 46, and projects inwardly into aligned bores 10 of the floating ring 8. A gap is provided between floating ring 8 and casing 46, so that a relative movement in the direction of the axis defined by pins 11 is possible. Stator member 2 is also supported for turning movement about the axis defined by the pins 12, for turning movement about the axis defined by the pins 11, and for axial movement with slide shoes 13 moving in guideways 7.

Stator member 2 has openings 15, 16, 17, and 18 which open in ports on the inclined surfaces 73, 72. These openings are used as inlets or outlets for a fiuid supplied to, or discharged from the chambers 39 to 42, the direction of the flow depending on the direction of rotation of the machine. In FIG. 2, a clockwise rotation is assumed, and consequently fluid is supplied under pressure through inlet openings 15 and 16, and is discharged through openings 17 and 18 if the machine is operated as a hydraulic motor. Corresponding inlets and outlet openings 23 and 24 are provided in casing 46, and also in the floating ring 8. Screw threads 19 to 22 are provided in the openings of casing 46 so that pipes can be attached to the casing. Communication passages connect the inner parts of the guide slots 302, 303 with the inlet and/ or outlet passages.

The openings in casing 46, floating ring 8 and stator member 2 are substantially aligned, and from inlet and outlet passages. However, as explained above, the stator member will perform slight movements relative to the floating ring 8, and the same will perform movements relative to the casing 46, so that it is necessary to provide inlet and outlet means maintaining the inlet and outlet passages fluid-tight since otherwise fluid would be discharged into the gaps between stator member 2, floating ring 8 and casing 46.

In accordance with the present invention, flexible tubular means are mounted in each of the inlet and outlet passages, and the fluid is supplied and discharged through passages in such tubular inlet and outlet means. The flexible tubular inlet and outlet means must be constructed in such a manner that they are capable of following all relative movements of members 2, 8 and 46 while providing in all positions a fluid-tight seal. It is preferred to construct the flexible tubular means of rigid parts which perform relative sliding movements.

Each of the inlet openings 15, 16, 17 and 18 has a planar annular abutment face 70 surrounding the respective opening and extending transverse to the longitudinal direction of the same. A sealing ring 27 has on one side a planar sealing face in contact with the corresponding sealing face 70, and at the other side a spherical annular seat 35.

Each opening 23, 24 in casing 46 has a planar annular abutment face 25 on which a sealing ring 27' is mounted. Each sealing ring 27 has an annular planar face 26 abutting the abutment face 25, and a spherical annular seat 28. An outer tubular sealing member 30, and an inner tubular sealing member 32 are telescopically connected and slide on each other on cylindrical surfaces 36. The outer sealing member has a spherical annular face 29 abutting said seat 28, and the inner tubular sealing member 32 has a spherical face 34 abutting the spherical seat 35. A spring 14 engages a flange 33 of sealing member 32, and an annular end face of the outer sealing member 30 and urges the sealing members apart in axial directions so that the sealing faces are pressed against each other. Transverse inner surfaces are provided in the region 31 between the outer and inner sealing members 30 and 32 so that the fluid within passages 37 urges the sealing members apart in axial direction.

It is evident that the spherical joints 28, 29 and 34, permit a tilting of the connected sealing members 30 and 32, that the sealing members 30. and 32 can move in a telescopic manner when stator member 2 moves toward or away from casing 46 in the direction of the axis of pins 12, and that rings 27 and 27 can slide on the corresponding planar faces 25 and 70 when stator member 2 moves in the direction of the axis of pins 11 toward or away from casing 46. In this manner, fluid-tight but flexible inlet and outlet means are provided so that the wobbling motion of the stator member 2 is possible, as required for producing a fluid-tight seal between the stator member 2 and the rotor during wobbling motions of the rotor.

' of the rotor.

as long as the forces exerted by the fluid on the rotor and stator member are counterbalanced and in complete equilibrium.

The fluid pressure in theexpanding and contracting chambers also acts on the surfaces 72, 73 surrounding the ports of the openings 15, 16, 17 and 18. The pressure of the high pressure chambers 39 and 41 prevails so that stator member 2 is urged to turn in counterclockwise direction. To prevent such rotation, stator member 2 would have to be particularly secured, but in accordance with the present invention, sealing rings 27 are formed with annular recesses 71, so that annular portions of the planar faces 70 are exposed to fluid pressure acting opposite to the fluid pressure in chambers 39 and 41 whereby the undesired torque acting on member 2 is compensated.

During operation as motor, the pressure fluid in chambers 39 and 41 will press against the center portions of the vanes 4 which are located in the recesses of stator ring 2, and in this manner a turning movement of the rotor will be caused. During this operation, the end portions 402 and 403 of the vanes 4 are reliably guided in slots 302, 303 of parts 102, 103 of the end members Slots 302, 303 are closed by the rings 79 which are secured in a suitable manner to end plates 59, 60 and to members 102, 103. However, it is also contemplated to make rings 79 integral with the end plates 59, 60. In the illustrated embodiment, the end plates 59 and 60 are secured by bolts 5 to the rotor members 102 and 103 and to the center part of the rotor, and corresponding bolts secure rings 79 to the-end plates 59 and 60.

As explained above, when the machine is used as a motor and turns in clockwise direction as viewed in FIG. 2, high pressure fluid is admitted through the inlet means associated with the openings 15 and 16 in stator member 2, while low pressure fluid is discharged through the outlet means associated with the openings 17 and 18 in stator member 2. The high pressure in the expanding chambers 39 and 41 produces opposite forces on the rotor as well as on stator member 2, such forces being completely counterbalanced due to the diametrical arrangement of the expanding high pressure chambers 39 and 41. Corresponding, but lower forces are produced by the low pressure chambers 40 and 42 and are also in equilibrium due to the diametrical arrangement of the low pressure chambers 40 and 42. It will be noted that, as a chamber 41 expands, and the surface area of the rotor exposed to high pressure increases, a corresponding expansion of the diametrically opposite pressure chamber 39 takes place so that the forces are counterbalanced in all positions of the vanes.

In the illustrated embodiment, each recess is divided into a high pressure and a low pressure chamber. However, instead of a single chamber for high pressure, and a single chamber for low pressure, a number of such high pressure chambers and low pressure chambers may be provided in each group of chambers.

In the illustrated embodiment, two high pressure chambers and two low pressure chambers are provided. However, it is also possible to provide a number of groups of chambers, for instance three groups of chambers spaced from each other 120 in circumferential direction,

or four groups of chambers spaced from each other 90. The groups of chambers may be spaced at different angles,

Springs 6 act on the vanes 4 in the region of the end portions of the same, where no strength is needed.

Consequently, it is possible to substantially narrow the end portions of the vanes whereby the provision of very long springs 5 is possible which is desirable to maintain the uniform spring force during a long radial stroke of the vanes. If the springs were provided in the region of the center portion of the vane, corresponding to prior art constructions, the springs would have to be very short, or the radial height of the vanes would have to be reduced to provide room for the springs, resulting in a weakening of the vane structure in the region where the fluid forces are effective. In certain modifications it will be possible to omit springs 6 while vanes 4 are moved radially outwards by their own weight, centrifugal force, or fluid pressure.

Vanes 4 are preferably provided with vane shoes 45 which project in circumferential direction from the vanes. Corresponding spaces 44 are provided in the rotor to permit the vane shoes 45 to be completely retracted in positions of the rotor in which the respective vane is not located in the region of a recess of stator member 2.

- Spaces 44 may extend into the lateral parts 102 and 103 of the rotor, or be provided only along the center part of the vanes which passes through the recesses in'stator 2. The vane shoes 45 have an outer end face in sliding and sealing engagement with the inner surface of stator member 2, and particularly with the part cylindrical surface portions 74 of the recess in stator member 2. The outer end portions 402 and 403 of the vanes are preferably shaped corresponding to the inner surface of the enclosing rings 79 which they abut under the action of springs 6 while the end faces of vane shoes 45 move along the surface 74 of the recesses in the stator member 2. Consequently, by suitably determining the inner diameter of rings 79, the clearance between the center portion of the vanes and the inner surface 74 of the recesses in stator member 2 can be determined. In the event that the machine is designed for low pressure, the clearance may be somewhat larger in order to reduce the friction. However, if the machine is designed for high pressure, such high pressure may deform rings 79, and increase the inner diameter of rings 79 permitting the vanes to move radially outward whereby the clearance between the vanes and the inner surface 74 will be reduced. In this manner, leakage through this clearance is prevented. The radial dimensions and the tensile strength of ring 79 must be suitably selected in order to obtain for the particular pressure the lowest leakage losses and the minimum of friction.

According to another feature of the invention, the radial slots 3, 302, and 303 are wider in circumferential direction than the vanes 4. Consequently, spaces 43 remain between one side of each vane, and the surfaces on one side of the slots 3, 302, 303. Spaces 43 form communication passages extending from the radial guide slots 302, 303 to the periphery of the center portion of the rotor. The pressure in chambers 41 and 39 urges the vanes to the proper position abutting the other surface of slots 3, 302, 303 and the part cylindrical surfaces 74 or rings 79 so that the vanes are properly guided for radial movement and travel along the part cylindrical surfaces. The provision of wider guide slots substantially reduces the cost of manufacture, since greater tolerances are permissible for the machining of the registering slots 3, 302, 303, and of the vane end portions 402 and 403. Moreover, the friction of the vanes within the guide slots is reduced. Nevertheless, the spaces 43 do not cause any leakage losses and do not reduce the high efliciency of the machine. Fluid can pass through spaces 43 thereby connecting the adjacent chamber 39, 40, 41 or 42 with the bottom of the respective guide slot 3. If no spaces 43 are provided, it is necessary to provide passages, not shown, for fluid between the respective chamber 39, 40, 41, 42 and the space in the respective guide slot 3 radially inwards of the respective vane 4 through rotor 1 or end members 59, 103, 79, 60, 102and/or 79, or other passages for fluid connecting the space in guide slots 3 within a space containing fluid under substantially the same pressure as prevails in the respective chamber adjacent the vane.

In order to reduce the friction between the end faces of the vanes and vane shoes, and the inner surfaces 74, balancing recesses 48 are provided in the end faces of the vanes 4 and vane shoe 45. Connecting ducts or channels connect the balancing recesses 48 with at least one radial surface of the respective vane, so that recesses 48 are connected with one of the chambers, for example into the contracting chamber 42, during passage of the vane through a recess in stator member 2. However, the balancing chambers may be connected by corresponding ducts to the high pressure chambers 41, 39. In this manner, a fluid cushion is formed between the vanes and the inner surface of stator member 2.

However, it is necessary that the fluid pressure acting on the vanes in radial outward direction exceeds the pressure of the fluid in balancing recess 48 and ducts 49. The area of the outer end faces of vanes 4, .vane end portions 402, 403 and of vane shoes 45 must be correspondingly designed. The clearance between the vanes and the inner surfaces 74 obtained by rings 79, and the connection of the balancing recesses 48 to the high pressure or low pressure chambers must also be considered. By suitably constructing these parts of the machine, a highly effective fluid-tight seal is obtained, while the friction between the vanes and the inner surfaces 74 is very low.

However, during movement of the vane end faces along the inclined surface portions 72, 73 of the recesses, a flush engagement between the vane end face 4a and the surfaces 72, 73 is not possible, and consequently some friction is produced, particularly along the surfaces 72, 73 which urge the vanes inwardly against the action of springs 6. This disadvantage is eliminated in a modified embodiment of the invention which is illustrated in FIGS. 3 and 4. As will be best seen by comparison between FIGS. 2 and 4, all basic features of the embodiment of FIG. 2 are also provided in FIG. 4, and consequently corresponding parts are indicated by like reference numerals. The vanes 4 of the embodiment of FIGS. 3 and 4 have no vane shoes, and the balancing recesses 48 with ducts 49 are omitted. Furthermore, the shaft portion 51 of rotor 1' is hollow and has an inner cylindrical surface 107. The lateral rotor parts 102 and 103', and the corresponding rings 79' are narrower than in the construction of FIGS. 1 and 2. The end members 59 and 60' are wider in axial direction, and end member 59 is formed integral with the shaft portion 51'. The springs 6 are omitted in the embodiment of FIGS. 3 and 4. The end members 59' and 60 are formed with cavities. Part of each cavity is a cylinder bore 61 or 62. Pistons 68 are located in each cylinder bore and are movable in radial direction therein. Radially extending closed slots 67 are provided in the walls between the cylinder bores 61, 62 and the slots 302 and 303' in the lateral rotor members 102' and 103'. The vane end portions 402' and 403 are not only guided in slots 302' and 303, but have narrow extensions 66 guided in the radial slots 67. Extensions 66 are connected by a slide seat or joint 69 to the respective associated pistons 68.

The outer endsof the cylinder bores 61, 62 are connected by short duct portions 64 to radial passages 63 which open in ports 63a on the inner surface 107 of shaft portion 51. The inner ends of cylinder bores 61, 62 are connected by other passages 65 to another set of ports 6511 which are spaced in circumferential direction about the inner surface 107 of shaft portion 51.

A stationary control valve member is provided in the hollow shaft portion 51 and has an outer cylindrical surface in sealing engagement with the inner surface 107. The control valve member has inlet and outlet ports and/or inlet and outlet passages or communication ports cooperating with ports 63a and 65a during rotation of the rotor, so that the ends of cylinder bores 61, 62 are alternately provided with pressure fluid, or connected to the discharge whereby the pistons 68 are reciprocated. The reciprocating pistons 68 move vanes 4 in outward and inward direction, and it will be understood that the actuation of the pistons can be timed in such a manner that the outer end faces of the vanes move along the inclined surfaces 72, 73 without any substantial pressure, or slightly spaced from the same. During movement of the vanes along the inner surface 74, the pistons are maintained stationary.

In a modified construction, not shown, the passages 63 and 65 open on the radial surface of a flange, and the control valve member has a corresponding surface formed with port and also located in a plane perpendicular to the axis of rotation.

The pressure of fluid in the inwardly located end portions of the cylinder bores 61, 62 will urge piston 68 outwardly while the vanes travel along the inclined faces 72, 73 of the recesses, but the speed of movement of the vanes in radial direction can be controlled in such a manner that the vane end faces remain very slightly spaced from the inclined faces 72, 73. After moving along surface 74, the vanes are again retracted at such a speed that no substantial friction exists between the ends of vanes 4 and the inclined faces 72, 73 of the recesses. It is preferred to prevent any frictional engagement between the vanes and the inner surface of the recesses, but to permit a small clearance filled by a fluid film. When the vanes have turned to a position in which they are no longer located opposite the recess, they are completely retracted into the rotor slots by the action of pistons 68, and maintained in this position so that no frictional engagement between the varies and the cylindrical inner surface of stator member 2 takes place. In constructions of the prior art where the vanes are under spring pressure, a continuous frictional engagement is unavoidable.

The joints or flexible connections 69 between the vanes and the piston are constructed in such a manner as to permit a limited tangential or circumferential, and preferably also axial relative movement between the vanes and piston, while preventing a relative radial motion between the vanes and the pistons. This permits a circumferential motion of vanes 4' into the spaces 43 of slots 3, 302 and 303, irrespective of the position of guide pistons 68. In this manner, the vanes can assume a position in which they are reliably guided by one radial surface of slots 3, 302, 303 for radial movement.

It will be understood that each of the elements described above, or two or more together, may also find a useful application in other types of rotary machines differing from the types described above.

While the invention has been illustrated and described as embodied in a fluid operated rotary. machine with diametrically arranged pressure chambers provided in a stator member capable of a wobbling motion and with vanes whose radial movement is controlled by fluid, springs or fluid operated pistons, it is not intended to be limited to the details shown, since various modifications and structural changes may be made without departing in any way from the spirit of the present invention.

Without further analysis, the foregoing will so fully reveal the gist of the present invention that others can by applying current knowledge readily adapt it for various applications without omitting features that, from the standpoint of prior art, fairly constitute essential characteristics of the generic or specific aspects of this invention and, therefore, such adaptations should and are intended to be comprehended within the meaning and range of equivalence of the following claims.

What is claimed as new and desired to be secured by Letters Patent is:

1. In a rotary machine, in combination, rotor means having a rotor axis and including a center portion having radial guide slots open at the periphery of said center portion, two end members having radially extending closed guide slots registering with said open guide slots to form with the same guideways and having confronting annular rotor guide faces, and vane means mounted for radial movement in said guideways; and stator means including an annular stator trnember surrounding said center portion and having two opposite annular stator guide faces respectively slidingly contacting said confronting guide faces of said end members, said stator member having intermediate said stator guide faces an inner annular surface surrounding said center portion and formed with at least two recesses equally spaced in circumferential direction having open ends closed by said end members, said recesses being successively passed by said vane means during rotation of said rotor means so that each vane means forms in each recess an expanding chamber and a contracting chamber, said stator means being formed with a pair of inlet and outlet passages for a fluid communicating with each of said recesses so that one of said chambers of each recess is filled with high pressure fluid and the other chamber of each recess is filled with.low pressure fluid, said expanding chamlbers being disposed diametrically opposite each other, and said contracting chambers being disposed diametrically opposite each other so that the inwardly directed pressures exerted on said rotor means by the fluid in said chambers are in equilibrium.

2. In a rotary machine, in combination, rotor means having a rotor axis and including a plurality of angularly spaced radially movable vane means, said rotor means including two end members; and stator means including supporting means, an annular stator memlber located between said end members surrounding said rotor means and having an inner surface formed with a plurality of recesses equally spaced in circumferential direction and having open ends closed by said end members, said recesses lbeing successively passed by said vane means during rotation of said rotor means so that each vane means forms in each recess an expanding chamber and .a contracting chamber, and mounting means for mounting said stator member on said supporting means non- ,turnable, but angularly tiltable about two axes perpendicular to each other and to the axis of rotation of said rotor means whereby said stator member is free to perform wobbling movements when said rotor means with said end members perform wobbling movements, said stator means having inlet means and outlet means for .a fluid communicating with each of said recesses so that one of said chambers of each recess is filled with high pressure fluid and the other chamber of each recess is filled with low pressure fluid, said expanding chambers being disposed relative to each other, and said contracting chambers being disposed relative to each other so that .the inwardly directed pressures exerted on said rotor means by said fluid in said chambers are in equilibrium.

3. In a rotary machine, in combination, rotor means having a rotor axis and including a center portion having radial guide slots open at the periphery of said center portion, two end members having radially extending closed guide slots registering with said open guide slots to form with the same guideways and having confronting annular rotor guide faces, .and vane means mounted for radial movement in said guideways; and stator means including supporting means, an annular stator member surrounding said center portion and having two opposite annular stator guide faces respectively slidingly contacting said confronting guide faces of said end members, said stator member having intermediate said stator guide faces an inner annular surface surrounding said center portion and formedwith at least two recesses equally spaced in circumferential direction having open ends closed by said end members, said recesses being successively passed by said vane means during rotation of said rotor means so that each vane means forms in each recess an expanding chamber and a contracting chamber, and mounting means for mounting said station member on said supporting means and including a floating ring surrounding said stator member, first means supporting said floating ring on said supporting means for angular tilting movement about a first axis perpendicular to said rotor axis, second means supporting said stator member on said floating ring for angular tilting movement about a second axis perpendicular to said first axis and to said rotor axis and for limited axial movement, said floating ring and said stator member being formed with inlet and outlet openings communicating with each of said recesses, and said stator means having flexible inlet means and flexible outlet means located in said inlet and outlet openings for supplying a fluid to said recesses so that one of said chambers of each recess is filled with high pressure fluid and the other chamber of each recess is filled with low pressure fluid, said expanding chambers being disposed relative to each other, and said contracting chambers being disposed relative to each other so that the inwardly directed pressures exerted on said rotor means by the fluid in said chambers are in equilibrium.

4. A rotary machine as set forth in claim 3 wherein said first means include a pair of pins secured to said supporting means and slidably supporting said floating ring, and wherein said second means include a pair of slide shoes, and a pair of pins secured to said slide shoes and slidably engaging said floating ring, said stator member having a pair of axially extending guideways slidably receiving said slide shoe means.

5. In a rotary machine, in combination, rotor means having a rotor axis and including a plurality of angularly spaced radially movable vane means, and two end a plurality of recesses equally spaced in circumferential direction, said recesses being successively passed by said vane means during rotation of said rotor means so that each vane means forms in each recess an expanding chamber and a contracting chamber, and means for mounting said stator member on said supporting means for limited movement at least in axial direction so that said rotor and stator guide faces move relative to each other in axial direction when said rotor means wobbles, said stator means having inlet means and outlet means for a fluid communicating with each of said recesses so that one of said chambers of each recess is filled with high pressure fluid and the other chamber of each recess is filled with low pressure fluid, said expanding chambers being disposed relative to each other, and said contracting chambers being disposed relative to each other so i that the inwardly directed pressures exerted on said rotor means by said fluid in said chambers are in equilibrium.

6. A rotary machine as set forth in claim wherein said supporting means includes a casing enveloping said stator member, said casing and said stator member being formed with aligned inlet and outlet openings, said inlet and outlet means being respectively located in said inlet and outlet openings and including means establishing a fluid tight sealing connection between said inlet and outlet openings in said casing and said stator member.

7. A rotary machine as setforth in claim 6 wherein said inlet and outlet means include flexible tubular members l'ocatde in said inlet and outlet opening and permitting relative movement between said casing and said stator member.

8. A rotary machine as set forth in claim 6 wherein each recess in said stator member is bounded by a cylindrical surface portion, and by two oppositely inclined axially extending surface portions at the ends of said cylindrical surface portion, said inlet and outlet openings having ports located on said inclined surface portions.

9. A rotary machine as set forth in claim 6 wherein said stator means includes a floating ring, means for mounting said floating ring for movement relative to said casing and said stator member, said floating ring being formed with inlet and outlet openings located between said inlet and outlet openings, respectively in said casing and in said stator member registering with the same and forming inlet and outlet passages with the same.

10. A rotary machine as set forth in claim 9 wherein said inlet and outlet means include flexible tubular members located in said passages.

11. A rotary machine as set forth in claim 10 wherein each of said flexible tubular members includes an outer sealing member and an inner sealing member in sliding sealing engagement with each other, one of said sealing members being in sealing engagement with said casing,

each of said inlet and outlet openings in said casing and' in said stator member has a planar annular abutment face, said inlet and outlet means including sealing rings, each sealing ring having a planar abutment face on one side in contact with one of said abutment faces and having a spherical seat on the other side, said outer and inner sealing members having at the free ends thereof spherical faces, said spherical faces slidingly abutting said spherical seats of two adjacent sealing rings whereby said tubular members are free to follow the relative movements of said stator member, floating ring, and casing while maintaining said passages sealed so that no fluid losses occur during passage of said fluid through said sealing members and sealing rings.

14. A rotary machine as set forth in claim 13 and including spring means for urging said outer and inner sealing members to move away from each other in axial direction and to fluid tightly about on said sealing rings whereby said sealing rings fluid tightly abut said planar annular abutment faces.

15. A rotary machine as set forth in claim 13 wherein said outer and inner sealing members have pressure faces arranged in such a position that fluid passing through said passagesurges said sealing members to move away from each other in axial direction thereof.

16. A rotary machine as set forth in claim 5 wherein .at least one pair of said annular guide faces are formed with recesses adapted to be filled with pressure fluid to form fluid cushions between said pairs of rotor guide faces and stator guide faces.

17. In a rotary machine, in combination, rotor means having an axis and including a center portion having guide slots open at the periphery of said center portion, two end members having cavities opening into said guide slots, said cavities each including a cylinder bore and duct means for supplying and discharging a fluid to and from said cylinder bore, and piston means mounted in said cylinder bores; vane means mounted for movement in said guide slots and having end portions located in said cavities of said end members and attached to said pistons so that said vane means can be moved inwardly and outwardly by operation of said pistons; and stator means including an annular stator member surrounding said center portion and having an inner annular surface surrounding said center portion and formed with at least one recess, said recess is successively passed by said vane means during rotation of said rotor means while said pistons control movement of said vane means so that the same move along the surfaces of said recesses; and control means for supplying fluid to, and discharging fluid from said duct means.

18. A rotary machine as set forth in claim 17 wherein said rotor means includes a hollow hub portion formed with an inner surface, said duct means having ports on said inner cylindrical surface, said control means including a control valve member located in said hollow hub portion and having control ports cooperating with said ports of said duct means to control the flow of fluid to and from said cylinder bores.

19. A rotary machine as set forth in claim 17 wherein said end members are formed with radial guide slots extending between said slots in said center portion and said cylinder bores, said end portions of said vane means passing through said radial guide slots and being guided in the same.

20. A rotary machine as set forth in claim 19 and including means on said end portions of said vane means and on said pistons for providing a flexible connection between said vane means and said pistons.

21. A rotary machine as set forth in claim 1 wherein said radial guide slots in said rotor center portion and in said end members are wider in circumferential direction than the vane means guided therein so that one side of said vane means is spaced from the opposite surface of the respective guide slots.

22. A rotary machine as set forth in claim 1 wherein said vane means having circumferentially projecting shoes at the outer ends thereof, each shoe and outer end of the respective vane means having an outer face adapted to slide on said inner surface of said stator member.

23. A rotary machine as set forth in claim 22 wherein said outer face of said vane means is formed with fluid receiving recesses, and with ducts connecting said recesses with at least one of said chambers to that a fluid cushion is formed between the outer ends of said vane means and said inner surface of said stator member.

24. A rotary machine as set forth in claim 1 wherein communication passage means are provided through the rotor means extending from the radial innermost part of said radial guide slots to and through at least one of the said confronting annular rotor guide faces.

25. A rotor machine as set forth in claim 1 wherein communication passage means are provided through the rotor means extending from the radial guide slots to and through the saidperiphery of said center portion of said rotor means.

26. A rotary machine as is set forth in claim 1 wherein communication passage means are provided connecting the radial innermost part of said radial guide slots and said inlet and/ or outlet passages.

27. In a rotary machine, in combination, rotor means having a rotor axis and including a plurality of angularly spaced radially movable vane means, and two end members spaced from each other in axial direction, said end members having a pair of confronting annular rotor guide faces; and stator means including supporting means, an annular stator member located between said rotor guide faces and having a pair of opposite annular stator guide faces opposite said rotor guide faces, respectively, said stator member surrounding a central portion of said rotor means and having an inner surface formed with a plurality of recesses, said recesses being successively passed by said vane means during rotation of said rotor means so that each vane means forms in each recess an expanding chamber and a contracting chamber, and means for mounting said stator member on said supporting means for limited movement relative to said end members of said rotor means so that said rotor guide faces and stator guide faces remain in sealing contact during movement of said rotor guide faces relative to said stator guide faces; and inlet means and outlet means for a fluid communicating with each of said recesses so that one of said chambers of each recess is filled with high pressure fluid and the other chamber of each recess is filled with low pressure fluid.

28. A rotary machine as set forth in claim 27 wherein said supporting means includes a casing enveloping said stator member, said casing and said stator member being formed with aligned inlet and outlet openings, said inlet means and said outlet means being respectively located in said inlet openings and outlet openings and including flexible tubular means establishing a fluid tight sealing connection between said inlet and outlet openings in said casing and said stator member, and permitting relative movement between said casing and said stator member.

References Cited by the Examiner UNITED STATES PATENTS 1,250,021 12/1917 Rubin 103--138 1,658,524 2/1928 Gurley 103136 1,871,525 8/1932 Hudson 103138 1,974,112 9/1934 Johnson 103138 1,988,213 1/1935 Ott 103120 2,149,337 3/1939 Deming 103136 2,371,081 3/1945 Tucker et a1 103-136 2,473,309 6/ 1949 Stephens 103136 2,808,004 10/1957 Durant et al. 103136 2,884,865 5/1959 Pettibone 103136 2,887,060 5/1959 Adams et al 103136 3,054,357 9/1962 McGill 103136 3,102,494 9/1963 Adams 103136 FOREIGN PATENTS 1,006,314 1/1952 France.

SAMUEL LEVINE, Primary Examiner.

JOSEPH H. BRANSON, Examiner.

R. M. VARGO, Assistant Examiner. 

2. IN A ROTARY MACHINE, IN COMBINATION, ROTOR MEANS HAVING A ROTOR AXIS AND INCLUDING A PLURALITY OF ANGULARLY SPACED RADIALLY MOVABLE VANE MEANS, SAID ROTOR MEANS INCLUDING TWO END MEMBERS; AND STATOR MEANS INCLUDING SUPPORTING MEANS, AN ANNULAR STATOR MEMBER LOCATED BETWEEN SAID END MEMBERS SURROUNDING SAID ROTOR MEANS AND HAVING AN INNER SURFACE FORMED WITH A PLURALITY OF RECESSES EQUALLY SPACED IN CIRCUMFERENTIAL DIRECTION AND HAVING OPEN ENDS CLOSED BY SAID END MEMBERS, SAID RECESSES BEING SUCCESSIVELY PASSED BY SAID VANE MEANS DURING ROTATION OF SAID ROTOR MEANS SO THAT EACH VANE MEANS FORMS IN EACH RECESS AN EXPANDING CHAMBER AND A CONTRACTING CHAMBER, AND MOUNTING MEANS FOR MOUNTING SAID STATOR MEMBER ON SAID SUPPORTING MEANS NONTURNABLE, BUT ANGULARLY TILTABLE ABOUT TWO AXES PERPENDICULAR TO EACH OTHER AND TO THE AXIS OF ROTATION OF SAID ROTOR MEANS WHEREBY SAID STATOR MEMBER IS FREE TO PERFORM WOBBLING MOVEMENTS WHEN SAID ROTOR 